Vanes for rotary vane machine supported in balance and in stability and in less friction



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INVENWKI KARL Em KMA/VA/ ATTOR'VEYS United States Patent 3,699,964 VANESFOR ROTARY VANE MACmE S U?- PORTED 1N BALANCE AND IN STABEITY AND IN LESFRICTEON Karl Eickmann, Talmuhle, Kreis Calw, Germany Filed Feb. 9,1959, Ser. No. 792,001 Claims priority, application Japan Mar. 13, 195322 Claims. (Cl. 103136) This invention relates to vanes of rotary vanemachines and more particularly to such vanes which are provided withextended slide portions -for stabilizing the movement of the vanes andeliminating the tilting of the vanes in their respective guide slotsduring operation. These vanes are further provided with recesses intowhich a pressure medium may be directed so as to produce counteractingforces to those exerted by the pressure medium tangentially to the rotorand normal to the lateral vane wall as well as those exerted radiallyoutwardly against the bottom vane wall. In this way, the vanes may bestably supported in their respective slots and the tangential forcecausing undesired tilting may be completely or at least partiallycounterbalanced. Heretofore, various vane constructions for rotary vanemachines have been used, although in such constructions there has beenundesirable tilting of the vane due to the unilateral tangential forceexerted thereagainst. Such tilting causes friction and wear along thelower trailing edges of the vane and slot as well as along the upperleading edges of the vane and slot. Previously, ttle importance wasattached to this tilting and the resultant friction and wear, sincerotary vane machines operating at low eificiency were consideredadequate.

A typical rotary vane machine is set forth in British Patent No. 744,446(Feb. 8, 1956) In that case, a rotary fluid-driven engine, either amotor or pump, is provided with vanes which slide in slots located inthe rotor and are enclosed by a casing ring, thereby definingcompression cells. Each cell during rotation of the machine as a motoradmits a fluid or pressure medium under pressure as the cell increasesin volume and releases the fluid or medium as the cell decreases involume, while in acting as a pump the cell draws in the fluid orpressure medium by suction as the cell increases in volume and expelsthe fluid or medium under pressure as the cell decreases in volume.Recently, however, the elimination of tilting and friction of the vanehas become increasingly important where the machine is required tooperate at high efdciency and with minimum frictional losses as is thecase with conventional unadjustable gear transmission machines.

It is an object of the present invention to provide a vane constructionfor rotary vane machines having means for stabilizing the vane duringrotation and tor counterbalancing the forces of the pressure mediumacting on the vane, whereby to permit tree floating travel of the vanein the guide slot and reduce friction and wear of the vane passingagainst adjacent parts.

Other and further objects will become apparent from a study of thespecification and accompanying drawings.

It has been found, in accordance with the present invention, thatfrictional forces and tilting forces of the vane as well as centrifugalforces and forces acting on the bottom side of the vane may be more orless completely balanced by corresponding counteracting forces. Thus,stabilized support of the vane during operation will reduce friction toa minimum and these counterbalancing forces will prevent any overloadingthat would otherwise cause undue wear.

Specifically, in accordance with the preferred embodiment of theinvention, the vane assembly is divided into 3,099,964 Patented Aug. 6,1963 a vane and a slide element. The slide element is located in achannel provided along the top edge of the vane and can rotate to alimited extent about its longitudinal axis in said channel. The topsurface of the slide element is constructed to smoothly abut the insidesurface of the casing ring against which it slides during rotation.Recesses are provided in the top surface of the slide element into whichthe pressure medium of the machine may be passed, so as to act againstboth the slide element and the casing ring and prevent friction. Inacting against the slide element and easing ring, a force is providedwhich completely or at least partially counter-balances the outwardradial forces exerted against the bottom of the vane in the slot and inturn transmitted radially outwardly to the slide element. In order toaccomplish this counterbalancing by means of so called pressure fieldscreated in the slide recesses and also to stabilize vane support, theslide element is preferably constructed oi greater width than the vane.Accordingly a larger area of contact with the casing ring surface isprovided which improves the supporting stability of the slide element.

Moreover, in normal rotary vane machine operation, the pressure mediumacts on the vane in one direction when the cell or intervane space actsas a compression cell or interva-ne space and in the opposite directionwhen the cell or inter-vane space acts as a suction cell or intervanespace. The vane travels more or less radially out wardly within the vaneslot provided in the rotor during rotation of the machine about one halfof the axis of rotation and then more or less radially inwardly withinthe slot during rotation about the other half of the cycle. During suchoperation in conventional rotary vane machines, the ressure medium actson the vane tangentially to the rotor, causing unilateral pressureagainst the vane during its travel within the slot. The frictionproduced by this one-sided force against the vane is considerable andconsequently reduces the efiiciency of the machine.

To overcome these drawbacks of conventional rotary vane machines,recesses are provided in the lateral sur faces of the vane into whichthe pressure medium may be transmitted by means of bore passages orchannels in the vane. These va-ne recesses are arranged in such a mannerthat the force or pressure fields produced by the pressure mediumtherein may be utilized to counterbalance the unilateral tangentialtorce acting against the opposite side of the vane. Upon reaching thisstate of counterbalance, the vane substantially floats in the guideslot.

Thus, in a construction according to the invention, metal contactbetween the vane and guide slot is almost completely avoided. Theunilateral force acting on one side of the vane is transmitted to theslot as well as to the rotor of the machine, and by means of the aboveconstruction creates counterbalancing pressure fields. Consequently,instead of metal acting on metal, the pressure medium acts on metal, andthe vane is free to float in the guide slot with a minimum of trictionand wear. Although internal friction caused by the molecules in ratstion in the fluid may still be present, this friction is comparativelynegligible.

The invention is further illustrated by the accompanying drawings inwhich:

FIG. 1 is a partial sectional view of a rotary vane machine taken alongthe line 11 of FIG. 2 and along the line 1-1 of FIG. 3.

FIG. 2 is a partial sectional view taken along the line 22 of FIG. -1showing the vane recesses.

FIG. 3 is a partial sectional view taken along the line 3-3 of FIG. 1showing the slide element.

FIG. 4 is a side view showing an embodiment of the vanes of a rotaryvane machine according to the invention.

FIG. 5 is a sectional view taken along the line 5-5 of FIG. 4.

FIG. 6 is a top plan view of the vane in FIG. 4, the view illustratingthe forces acting on the vanes in tangential direction to the rotor, andthe balancing pressure fields counteracting said forces.

FIG. 7 shows a partial section taken along the line 6-6 of FIG. 4.

FIG. 8 is an enlarged view of a partial section taken along the line 2-2of FIG. 1, showing the end portion of the vane positioned in the slotdefined by the side-walls of the rotor, the view illustrating the actingforce in tangential direction and the balancing pressure fields incounter direction where the vane has moved slightly outwardly in aradial direction within the slot.

FIG. 9 is a sectional view similar rto FIG. 8 showing the vane furtheroutwardly positioned in a radial direction the slot of the rotor andindicating the consequent existence of greater forces.

FIG. 10 is an enlarged view of a partial section taken along line 3-3 ofFIG. 1 showing the force of the vane and of the slide element producedin a radial direction and the balancing of these forces by means ofcorresponding counter pressure fields.

FIG. 11 shows an embodiment of the vane slide ele ment.

FIG. 12 is a sectional view taken along the line 12-12 of FIG. 13.

, FIG. 13 is a top view of the vane slide element of FIG. 11.

FIG. 14 shows an embodiment of the assembly of the vane and the vaneslide element.

FIG. 15 is a sectional view taken along the line 15-15 of FIG. 14.

: FIG. 16 is a top view of FIG. 14.

FIG. 17 is a sectional view of a further embodiment of the rotary vanemachine illustrating additional mechanical details.

FIG. 18 is a partial sectional view taken along the line 18-18 of FIG.17.

FIG. 19 is a sectional view of a further embodiment of the rotary vanemachine.

FIG. 20 is a partial sectional view taken along line 20- 20 of FIG. 19.

FIG. 21 is a further embodiment showing the vane slide elementcomprising two separate members.

FIG. 22 is a sectional view taken along the line 22-22 of FIG. 21.

FIG. 23 shows a rotating part of the vane slide element of FIG. 21.

FIG. 24 is a sectional view taken along the line 24-24 of FIG. 23.

FIG. 25 shows a sliding member of the slide element in FIG. 21 havingbalancing pressure field recesses.

, FIG. 26 is a sectional view taken along the line 26-26 of FIG. 25.

FIG. 27 shows a further embodiment of the vane slide element comprisingtwo separate members.

FIG. 28 is a sectional view taken along the line 28-28 of FIG. 27.

- FIG. 29 shows a rotating member of the vane slide element of FIG. 27.

FIG. 30 is a sectional view taken along the line 30-30 of FIG. 29.

FIG. 31 is a top view of the sliding member of FIG. 27

FIG. 32 is a sectional view taken along the line 32-32 of FIG. 31.

FIG. 33 is another embodiment :of the vane having a slide elementcomprising two separate members.

FIG. 34 is a sectional view taken along the line 34-34 of FIG. 33.

FIG. 35 is a side elevation view of the vane shown in FIG. 33 with theslide element removed.

FIG. 36 is a sectional View taken along the line 36-36 of FIG. 35.

FIG. 37 is a side view of the separate rotating member of the vane slideelement of FIG. 33.

FIG. 38 is a sectional view taken along the line 38-38 of FIG. 37.

FIG. 39 is a side view of the separate sliding member of the vane slideelement of FIG. 33.

FIG. 40 is a sectional view taken along the line 40-40 of FIG. 39.

FIG. 41 is a side elevation view showing another embodiment similar tothat of FIG. 33.

FIG. 42 is a sectional view taken along the line 42-42 of FIG. 41.

FIG. 43 is a side elevation view of the vane of FIG. 41 with the slideelement removed.

FIG. 44 and FIG. 45 show sectional views taken along the line 44-44 and45-45 of FIG. 43, respectively.

FIG. 46 and FIG. 47 show a side view and sectional view of the rotatingmember of the vane slide element of FIG. 41, respectively.

FIG. 48 and FIG. 49 show a side view and a sectional view of the slidingmember of the vane slide element of FIG. 41, respectively.

FIG. 50 is an embodiment of the vane in which the rotating member of thevane slide element is covered by a separate bearing cover.

FIG. 51 is a sectional view taken along the line 51-51 of FIG. 50.

FIG. 52 is a side elevation view of the vane shown in FIG. 50 with theslide element removed.

FIG. 53 and 54 show sectional views taken along line 53-53 and 54-54 ofFIG. 52, respectively.

FIG. 55 and FIG. 5 6 shows a side elevation view of the bearing coverand a sectional view taken along the line 56-56 of FIG. 55, of theembodiment in FIG. 5 0 respectively.

FIG. 57 and FIG. 58 are a side view and -a sectional view of a pin inFIG. 50.

FIG. 59 and FIG. 60 are a side view and a sectional view of the rotatingmember of the vane slide element of the embodiment in FIG. 50,respectively.

FIG. 61 and FIG. 62. are a side View and a sectional view of the slidingmember of the vane slide element of the embodiment shown in FIG. 50,respectively.

FIG. 63 is a side View of the vane and slide element showing a 'furthermeans for receiving the slide element in the vane.

FIG. 64 is a cross section along the line 64-64 of FIG. 63.

FIG. 65 is a side view of the vane shown in FIGS. 63 and 64 with theslide element removed.

FIG. 66 is a cross section along the line 66-66 of FIG. 65.

FIG. 67 is a side view of another embodiment of the invention showingadjustable vane recesses for conrespondingly adjusting the balancingpressure fields.

FIG. 68 is an enlargement of a cross-sectional view taken along the line68-458 of FIG. 67 illustrating the manner of adjustment of the vanerecesses.

Referring to the drawings, in FIGS. 1, 2, and 3, 1 represents a controlshaft of a rotary vane machine, 2 is the rotor, and 3 represents boresguiding radially outwardly and inwardly the pressure medium to and fromthe slot space below the vane through the control shaft. 4 is a channelguiding outwardly the pressure medium from the rotor during eachrevolution of the machine. 5 is a shaft driving the rotor. 6 is a casingring. 7 and 8 are extended portions of the vane slot defined by the sidewalls of the rotor. 7a and 8a are pressure medium chambers locatedradially in the vane slot above the vane. 9 and 16 are side-coverssealing axially and radially the side wmls of the rotor. 11 are vanes ofthe rotary vane machine and '12 is a slide element thereon. 13 is anextended rotatingmernber of the slide element adjacent the side wall. 14is an extended portion of the vane located along the side wall androtating therewith. 15 and 16 we U-shaped portions located on theextended portions of the vane with bucklings to prevent the slidepositioned therewithin from falling out of the vane. 17 and 18 arebalancing pressure recesses provided in the vane. 17:: md 18a arecorresponding balancing pressure recesses provided separately in thevane. 27 is a balancing pressure recess in the slide. 28 is a pressuremedium chamber located radially and inwardly of the vane. 29 is apassage in the rotor for guiding the pressure medium into and out of thevane cells or intervane spaces. 36 and 39 are two adjacent vane cells orintervane spaces. These cells or intervane spaces are the vane chambersof the rotary vane machine.

In FIGS. 4, 5, 6 and 7, 11 is the vane, 14 is the extended side portionof the vane adjacent the side wall of the rotor. 15a is an inner bentbuckling along the top edge of the vane preventing the slide fromfalling out of its vane seat. 17, 17a, 13, and 13a are balancingpressure recesses in the vane. 19 and 29 are additional balancingpressure recesses in the vane, opposite corresponding balancing pressurerecesses 19a and 26a, not shown. 23 is a bore channel guiding thepressure medium into the balancing pressure recess 19. 21, 22, 2d, 25,and 26 are bore channels for correspondingly guiding the pressure mediumto balancing pressure recesses 29, 26a, 18a, 18, and 17. 31 shows theworking medium under pressure acting on the vane in the direction of thearrow c. 32 and 33 show the balancing pressure fields created in thevane recesses on the opposite side of the vane and the working directionof the counteracting pressure in the balancing pressure fields.

In FIGS. 8, 9 and 10, 2 is the rotor. '11 is the vane. 12 is the slideelement; 6 is the casing, and 10 is the side wall sealing cover. 40 and42 are radial pressure chambers inwardly to the vane, and 45 is a radialpressure chamber outwardly to the vane while 46 is a buckling of thevane. 39 is a vane cell or intervane space. 33 and 34 show the workingmedium under pressure acting on the vanes in different radial positions.32, 35, and 36 show the pressure medium in the balancing pressurerecesses counteracting the working pressure. 44 and 38 are widened slideends providing a stabilized support for the slide. 6 shows the pressuremedium acting radially and outwardly on the vane. 37 shows the balancingpressure field created in the slide element recesses which counteractsthe pressure in 46.

In FIGS. 11, 12 and 13, 51 and 52- are rotating members of the slideelement extended to fit adjacent the side wall of the rotor. 6 is thesliding surface of the sliding element adapted to slide along the casingring. 53 is a balancing pressure recess provided in the slide element.

In FIGS. 14, l and 16, 11 is the vane and 15 and 16 are extended sideportions of the vane, which are fitted into the side walls of the rotordefining the slots, and are inwardly bent to prevent the slide elementfrom falling out. 56 is the sliding member of the slide element and 53is a balancing pressure recess. 51 and 52 are rotatable extendedportions of the slide element in the extended parts of the vane.

In FIGS. piston machine and 17, 18, 19 and 20, 2 is a rotor of therotary 6 is the casing ring. 54 and 55 are slide sealing walls. '11 isan embodiment of the vane and 12 is a slide element. 60 is the rotatingmember of the slide element. 57 and 56 are guide rings urging the vanesradially and outwardly. 63 is a roller rotating over rings 56 and 57 and61 is a pressure spring forcing the slide element against the casing. 62is a spring case surrounding spring 61 to prevent the spring frombecoming dislodged, and transmitting the spring pressure to roller 63.58 and 59 are sliding shoes fitted radially within the vane and areslidable on guide rings 56, 57. In this embodiment of the invention,radial projections are located on shoes 58, 59 to prevent the shoes fromaxial movement between guide rings '56, 57 and side walls 54, 55.

In FIGS. 21, 22, 2 3, 24, 25, 26, 27, 28, 29, 30, 31, and 32, 6'5, 66,69, and 76 are rotating members of bipartite slide elements which permitthe slides to rotate in the vanes. 64, 67, 68, and 71 are the slidingmembers of various types of bipartite slide elements. The slide elementsrotate with these sliding members passing along the casing ring. 77 76,74, and 73 are balancing pressure recesses provided in the slideelements. 72 and 75 are grooves in the sliding members for fittingtherein the rotating members upon joining the two slide memberstogether.

In FIGS. 33 to 40, 78 is a vane, 79 is a rotating member of the vaneslide element and 80 is a sliding member of the slide element. 81 is abore in the vane for supporting the rotating member of the slide elementand 82 is a slot provided in the top face outwardly to the bore andradially to the vane. '83 is a bore provided in the sliding member ofthe vane slide element to fit therein the rotating member of the slideelement.

In FIGS. 41 to 49, 84 is a vane, '85 is a rotating member of the slideelement and 86 is a sliding member of the slide element. 87 is a boreprovided in the vane to pivot the rotating member of the slide element,and 88 is a bore in the sliding member of the slide element forinsertion of the rotating member.

In FIGS. 50 to 62, S9 is a vane, 90 is a rotating member of the vaneslide element and 91 is a sliding member of the slide element. 92 is abore provided in the vane to pivot the rotating member of the slideelement. 93 is a groove provided above bore 92 along the extended vaneportion radially to the wane for securing bearing cover 94. 95 and 96are pin holes provided on the vane and the bearing cover for insertionof a pin 97 to connect vane 89 and bearing cover 94.

In FIGS. 63 to 66, 98 is a vlane, and the slide element comprises arotating member 99 and a sliding member 160. 101 is a slot provided atthe side end extension of the vane for supporting the rotating member ofthe slide element.

In FIGS. 67 and 68, 102 is the vane, 193 is the sliding member of theslide element, and 104- is the rotating member. 105 is the enclosingring, 106 is the side Wall of the rotor, and 107 is the sealing cover ofthe side wall of the rotor. 108 is the rotor. 109 is the balancing pressure recess provided on the side face of the vane and 110 is the sealingplate sealing from below the balancing pressure recesses. 111 is the pinfixing the sealing plate on the side face of the guide slot and rotorside wall. 113 is the conduit connecting the balancing pressure recessto the vane cell on The invention is more In FIGS. 1, 2, :and 3, thedisposition of the vanes and slide elements in the rotary vane machineand the position of the balancing pressure recesses are shown. Vanes 11slide in radial guide slots 8 and 7 provided in rotor 2 and revolvetogether with the rotor. The rotary vane machine is enclosed by easingring 6 and upon rotation vanes 11 are thrown radially outwardly bycentrifugal and other forces, so that slide element 12, positioned onthe top portion of the vane abuts the inside surface of casing ring 6and slides along the casing ring.- In this way variable volume workingcells are formed between casing ring 6, vanes 11 and slide elements 12,and side covers 9, 101 sealing axially and radially the rotor and sidewalls. During each revolution of the rotor, vanes 11 and side elements12 travel radially inwardly and outwardly, so that the capacity ofworking cells or intervane spaces is increased and decreasedaccordingly. Two adjacent working cells or intervance spaces are shownin positions 30 and 39 in FIG. 3. These cells or intervane spaces takeup the working medium by means of distribution shaft 1 through thepassages 29 during one half of the cycle and force the medium outthrough another passage of the distribution shaft 1 during the fullydescribed by the followthe opposite side of the vane.

second half of the cycle. The rotor is driven by driving shaft 5, andthe pressure medium leaves the rotor through bores 4. Passing throughchannels -3, the pressure medium enters slot chamber 2 8 radially belowthe vane through the distribution shaft. In these slot chambers, thepressure medium acts on the vane bottom forcing the vane radiallyoutwardly. The vanes are shorter than the length of the slots located inthe side walls or are provided with radial bores or slots, so that thepressure medium may either flow radially and outwardly along the lateralends of the vanes, or may flow through the radial bores in the vanes,thereby reaching chambers 7a or 8a, located radially Within the slotsand above the vanes. An essential feature of (the invention concerns thepassage of the pressure medium as from chambers 7a, 8a into thebalancing pressure recesses 27 provided in slide elements 12. In thesebalancing pressure recesses of slide element 12, a pressure field isproduced and the pressure medium is directed radially inwardly, towardthe vanes to counteract the radial outward pressure in slot chamber 28,and the centrifugal force acting on vane 11. This counteracting fieldcompletely balances the pressure force on the vane bottom from chamber28 as well as the acting pressure force and centrifugal force, so thatthe vane in radial direction is completely free from or is only slightlyeffected by the hydraulic pressure force, acting pressure force, andcentrifugal force. Even when the pressure of the medium is very high,the vanes are pressed radially and inwardly by said sliding elementpressure field, so that compression between the vane and the casing ringor between the slide and the casing ring does not occur. Any overloadingis therefore automatically prevented.

Where the rotary vane-machine serves as a motor with pressure mediumrevolving in the direction of arrow B, as shown in FIG. 3, vane 11 isforced by the working pressure in the cell 30 to rotate the rotor in thedirection of arrow B. The pressure medium passing through bores 23, 21and 25, 26 in the vane, enters the balancing pressure recesses 20, 19and 18, 17 from the cell 30. Consequently, the balancing pressurerecesses 17, 18 and 19, 120 positioned in the extended side portion ofthe vane within the slot of the rotor are effected by similar pressureon the other side of the vane ahead of cell 30, and the pressure inthese balancing fields is directed oppositely to the pressure in thedirection of arrow B in cell 30, thus balancing completely or partiallythe working pressure in the direction of arrow B. In this Way, pressureload of vanes 11 within the slots is reduced completely or partially,and the vane travels freely in the pressure medium between the walls ofthe slot. While the balancing pressure recesses have been divided into17 and 18, many balancing pressure recesses may be used so as toincrease or decrease in any desired manner the pressure of the balancedpressure field in accordance with the degree of radial travel of thevane.

Contrastly, where the rotary vane machine serves as a pressure pumprotating in the direction of arrow B, the medium pressure is produced incell 39, exerting a tangential pressure on vane 11 in the direction ofarrow A. This pressure is balanced by the balancing pressure fieldscreated in recesses 17a, 18a, 19a, and 20a. The pressure medium flows tothe balancing pressure recesses 17a and 18a through bores 24 and 24a andto the balancing pressure recesses 19a and 20:: through bores 22 and22a. This action of force is applicable similarly to all vanes 11 andslide elements 12 in corresponding positions of the rotor.

By extending considerably the vane ends 14 into slot chambers 7, 8 aspace is produced which is sufiiciently large for the balancing pressurefields created within the vane to balance the tangential pressure actingon the vane to any desired extent by bending over edges 15a, 16a of thevane, slide elements 12 cannot become dis- 8 lodged, as rotating member13 is inserted below the bent portions of the vane.

FIGS. 4, 5, 6 and 7 show the recesses creating the balancing pressurefields counteracting the tangential force against the vanes; thedisposition of bores guiding the pressure medium into the balancingpressure fields; the working pressure acting on the vanes; and thepressure in the balancing pressure recesses acting upon the vanes. Vane11 has extended portions 14 with which it is fitted in the side walls ofthe rotor. An essential feature of the invention comprises providing inextended portions 14 recesses such as 17, 18', 19, 20, 17a, 18a, 19a and20a or many further recesses suitably disposed for receiving thepressure medium therein. The pressure medium acting upon the oppositeface of vane 11 is guided through corresponding bores to these recesses.31 indicates the working pressure acting 'on the vane in the directionof arrow C. This pressure is transmitted to the balancing pressurerecess 213a through bore 21 as shown in FIG. 7, and like wise to thebalancing pressure recess 18a through bore 25. Similarly, balancingpressure recesses 19a and 17a are effected by the pressure mediumthrough the bores 23 and 26. 31 in FIG. 6 shows the Working pressureacting on the vane in the direction of arrow C. 32 and 33 show thepressure acting upon the vane in the balancing pressure fields. As isapparent in FIGS. 6 and in the aforesaid manner, the force of theworking pressure acting on the vane is completely balanced by the sumofthe orces in opposite direction produced in the individual balancingpressure fields via the recesses.

Where the rotary vane machine is employed in the reverse manner ofoperation, the pressure at 31 in FIG. 6 acts on the opposite side of thevane and in opposite direction to that of arrow C. Thus, the pressure isnot guided to the balancing pressure recesses 17a, 18a, 19a and Zea, butinstead to the balancing pressure recesses l7, l8, l9 and 20 throughcorresponding bores, and this pressure acts on the sides opposite faces32 and 33 and in opposite direction.

The larger the outward radial movement of the Vane in the slot, the morewill be'the working face of the medium. In FIG. 8, the working medium iseffected only in plane 33, since the vane moves slightly radiallyoutwardly within the slot. In this case, as shown in FIG. 4, bores 21and 25 are still covered by the slot of the rotor, and only recesses 17aand 19a create the balancing pressure fields shown at 32'. In FIG. 9 thevane has traveled further radially outwardly, and bores 21 and 25 inFIG. 4 are positioned externally to the slot of the rotor and abut cell39 of FIG. 3. In this position, as shown at 34 in FIG. 9, the tangentialworking pressure acts on vane 11 while the balancing pressure fieldscreated act in the direction indicated by the pressure arrows 35 and 36.

Although the embodiment shown employs two separate balancing pressurefields at each vane extension, many steps of fields may be used so thatthe balancing pressure fields and their action increase continuously asthe vane travels radially outwardly of the slot. FIG. 10 shows a mannerof balancing the radial fluid pressure acting upon the vane bottom. Thepressure medium is guided into inner cell 49 beneath the vane and withinthe slot of the rotor. The pressure medium is also present in cell 45positioned radially outwardly of the vane within the side walls as shownin FIGS. 8 and 9'. Cell 45 is connected directly with the balancingpressure recesses provided in the slide element. If the area of pressurefields 40 and 37 are the same, the force produced at area 40 will beequal to the force produced at area 37. In this way, the forces in thepressure medium acting radially outwardly upon the vane bottom andinwardly upon the slide element are in balance and the vane, inarrangement with the slide element, freely floats between casing ring '6and rotor 2. Where field area 37 is greater than area 40, any frictioncaused by the centrifugal force is offset, under a given pressure in thepump. 44 and 38 show extended surface portions or the sliding member.These portions provide a stable support and a stable sliding of theslide element along casing ring 6, and further, these port-ions performa sealing action between balancing pressure field 37 in FIG. 10 and thepressure in the working cells of the individual vanes. Rotor 2 has agroove 39 shown in FIG. 10 to fit therein sliding parts 44, 38, wherethe vane travels radially inwardly.

Constructions of other embodiments of the slide element of the inventionare illustrated in section in FIGS. 11, 12, and 13. The essentialcharacteristic of the slide element in these embodiments is therevolving member which has the same radius as the channel on the topsurface of the vane, so that the slide is rotatable around its axis inthe channel. The sliding member of the slide element is constructed sothat it abuts the side walls of the rotor and slides along the width ofthe casing ring; the wider sliding part of the slide being adapted tofit closely within a recess in the side wall of the rotor. Thesebalancing pressure fields created in the slide element recesses mayresult from many recesses or even from one recess.

FIGS. 14, 15 and '16 show a manner of fitting the slide element ontovane 11. Slide member t} rotates with rotating members 51, 52' insertedinto the vane, edges 15, 16 of the vane are bent inwardly so that theslide may not become dislodged from the vane. The sliding member of theslide element is closely fitted between the extended side :portions 15,16 of the vane 11, sealing the space between sliding member 5% and sideedges 15 and 16 of the vane. I

FIGS. 21 and 22 show a constructional form of the slide elementconsisting of two separate members. Sliding member 64 has a groove 75into which rotating member 66 can be inserted and secured. FIGS. 23 and24 show a form of the rotating member. FIGS. 25 and 26 indicate a formof the sliding member. The halved rotating member shown in FIGS. 21-26has a particular advantage in that it can simply be constructed bygrinding a cylindrical pin to form a halved member as shown in FIG. 24.Another advantage is that the rotating memher, as a separate member, canbe made so that its length is very accurate. In this way, it can beinserted snugly into the extended side part of the vane shown in FIG.14. Furthermore, the construction of the slide element in two partsmakes it possible to fit the rotating members into the vane, turn inedges 15, 16 (FIG. 15), and later secure the sliding member thereonseparately.

The constructional form of the slide members shown in FIGS. 27, 28, 29,30, 31 and 32 has similar advantages to those of the two-piece slideelement shown in FIGS. 21-26. Thus, the rotating member is merely ashafit 69, 70 in ground cylindrical form, which is simply inserted intogroove 72 of sliding member 71. 73 is a balancing pressure recess.

The two-piece slide element shown in FIGS. 27-32, however, can only beemployed where the vane and slide are forcibly directed between casingring 6 and guide rings 56, 57 as shown in FIGS. 17, 18, wherein rotatingmember 60 of the vane slide element is simply fitted into both groovesof vane 11 and slide member 12. In the embodiment shown in FIGS. 17, 18,it is not necessary to protrude the vane into the side Wall.Consequently, this construction can be applied generally to vanes forconventional pumps. In this case, the pressure medium is directed to thebalancing pressure recess 86 from working cell 84 through bore 85 insliding member 12. Bores are provided radially in vane 11, andcompressed springs 61 are disposed in these bores. Each spring isencircled by a spring case, 62, pressing the case radially and inwardly.Spring case 62 has an opened sliding bearing in a semi-cylindrical formenclosing running roller 63'. Roller 63 has a turning groove, into whichthe hearing of the spring case 62 is fitted. By this fitting, thesliding speed between the spring case 62 and the running roller 63 canbe kept at a Passages are turned in the rotor or in the side wall of therotor tor receiving guide rings '56 and 57. Running roller 63 revolvesover guide rings 56, 57. In other embodiments, running roller 63 isdivided into two sections. The vane and the slide may be constructed ofsuch accurate dimensions that the spaces between individual parts are sosmall that sliding roller 60 cannot become dislodged from the slide andvane assembly. Slight tolerances in manufacture are compensated byspring 61 which constantly keeps these parts in tension radially betweenrunning rings 56, 57 and the casing ring.

In FIGS. 19 and 20, another embodiment is illustrated for guiding thevane and slide element forcibly between casing ring 6 and inner runningrings 56, 57. A means of keeping the vane and slide assembly forciblyunder tension between the casing ring and the guide ring is essentialfor all vane and slide assemblies having balancing pressure recessesWhere no means for preventing the slide element from falling out of thevane are provided.

In the embodiment shown in the FIGS. 19 and 20, sliding shoes 58 and 59are inserted into a groove in the bottom face of vane 11 radially andinwardly to the ends of the vane. Sliding shoes 58, 59 slide on theirunder side along running rings 56, 57 as slide element 12 travels alongenclosing ring 6. These inner sliding shoes 58, 59 have as an importantfeature radial projections provided on the plane thereof which partiallyencircle guide rings 56, 57, being positioned between guide ring 57 andsidewall 55 or between guide ring 56 and side wall 54. These projectionsprevent radial movement or axial displacement of the related parts.

FIGURES 33 to 40 FIGURES 41 to 49 and FIGURES 50 to 62, respectively,show various improved embodiments according to the invention in whichengagement between the sliding member and the rotating member of thevane slide and engagement between the rotating member and the vaneitself permit advantageous employment of bipartite slide members asshown in FIG. 28. These embodiments are simple to manufiacture andprovide an improved sealing condition between adjacent vane cells.

In FIGURES 33 to 40, rotating member 79 of the vane slide is simplyconstructed as a cylindrical rod, more than half the face of which isenclosed :by sliding member 80 of the vane slide upon assembly so thatthese members cannot be separated. Furthermore, rotating member 79 ispivoted within bore 81 in the extended portion of the vane which slideswithin the guide slot of the rotor side wall. Consequently, -no leakagecan occur between adjacent vane cells caused by lifting rotating member79 from its channel along the top face of vane 78. The bore 81 of thevane is constructed of a slightly smaller diameter than that of therotating member 79. Slot 82, disposed between the outer radial end facesof the extended portion of the vane permits rotating member 79 of thevane slide to be slid into bore 81 where it is received under tension.

FIGURES 41 to 49, respectively, show an embodiment similar to those inFIGURES 33 ltO 40, but without provision for a slot. In this embodiment,rotating member 85 of the vane slide is merely pushed and fitted intobore 87 of vane 84. Other features are similar to those of FIGURES 33 to40.

In the embodiment shown in FIGS. 50 and 52, the halved bearing system,instead of the bore-bearing system, is employed. In this case, rotatingmember 90 of the vane slide is sustained in the semi-cylindrical shapedgroove 92 of vane 89, land is covered by hearing cover 94 from above.Bearing cover 94 is inserted into groove 93 provided at the top face ofthe extended portion of the vane and is secured to the vane by pin 97which is inserted through pin holes 95, 96. Rotating member 90 andsliding member 91 of the slide element are similar to those shown inFIGS. 33 to 40 and FIGS. 41 to 49.

FIGURES 63 to 66 show an embodiment of a further means for receiving thevane slide. In this embodiment, a groove 101 is arranged at an angle ofabout 30 to 45 degrees with respect to the side of the vane, at theextended portion of vane 98. The slide element, consisting of rotatingmember 99 and the sliding member 100, is inserted into the groove 101and rotatably supported via both ends of rotating member 99. In itslocation, within the guide slot of the rotor, the extended portions ofthe vane are positioned adjacent the side wall of the rotor, and theopenings of slot 101 are sealed by the side walls so that the slideelement cannot become dislodged during operation.

In the embodiment shown in FIGS. 67 and 68, balancing pressure recess109 provided on the extended portion of vane 1-0-2 'is open on itsbottom side and may be enlarged downwardly toward the lower end of thevane upon radial outward travel of the vane within slot 112. In order toseal the open end of the recess in a downward direction, sealing plate110, which is adapted to slidably and tightly close recess 109 duringthe radial inward travel of vane 102, is provided on the side face ofthe slot 112 of rotor side wall 106 in direct line with recess 109.Plate 110 may be suitably secured, as vfor example, with a pin 111.Thus, during operation of the rotary piston machine, all sides of thepressure recesses creating the counter balancing pressure fields aretightly sealed, allowing entry and exit of the pressure medium onlythrough ducts 113 to similar recesses on the opposite side of the vane.The counter pressure fields created, balance the vane in the slot andpermit the vane to float radially inwardly and outwardly during eachmachine cycle with a minimum of friction, tilting and wear.

In the last mentioned embodiment, during rotation of the rotor, thebalancing pressure field created increases and decreases accordingly asthe vane moves in and out of the slot, affording a more completebalancing action than the step-like action which takes place whereseparate recesses are provided in the extended portion of the vane.

It will be obvious to those skilled in the art that while thespecification and drawings have been set forth herein to illustrate theinvention, various changes and modifications may be made withoutdeparting from the spirit and scope of the invention, which is to belimited only by the appended claims.

What is claimed is:

1. A rotary vane type engine comprising a casing having an innercircumferential surface defining -a working chamber for receiving anddischarging fluids, a rotor in said working chamber having an axiseccentric with respect thereto and provided with radial slots, vanessubstantially radially slidable in said rotor slots and forming withsaid rotor and with said working chamber, expanding and contractingintervane spaces in which said fluid is received, said rotor extendingin said casing axially beyond the axial ends of said Working chamber andsaid rotor slots in said rotor extending axially beyond the ends of saidworking chamber, a slide element rockingly mounted longitudinally oneach vane for rocking about a longitudinal axis, said slide elementhaving a radially outer side adjacent yet spaced from the casing innersurface and opposed edges extending substantially radially outwardlytherefrom in said working chamber to said surface and axially to theends of said working chamber to maintain sealing contact with saidsurface and to form therewith and with said radially outer side of saidslide element a balance chamber for the reception of pressure fluid, anda passage external to said vanes through the portion of' the rotor slotextending beyond the ends of the working chamber to provide opencommunication at all times between such balance chambers and the bottomof said rotor slots for the passage of pressure fluid from the bottom ofsaid rotor slots to said balance chambers.

2. Engine according to claim 1 wherein said vanes are axially wider thansaid intervane spaces and are wholly 12 contained at their ends in saidrotor slots, and said balance chambers extend to the axial ends of thevane portions within said working chamber and are axially openended forcommunication with the bottom of said rotor slots external to saidvanes.

3. Engine according to claim 1 wherein said passage is continuously incommunication with the pressure side of the rotary vane type engine toreceive fluid at the maximum pressure within the casing.

4. Engine according to claim 1 wherein said passage is common to allsaid rotor slots.

5. Engine according to claim 1 wherein said rotor extends beyond saidworking chamber laterally and radially at its ends and said vanes alsoextend laterally beyond said working chamber, said balance chambers attheir axial ends communicating with said rotor slots.

6. Engine according to claim 5 wherein the lateral extensions of saidvanes slide in corresponding lateral extensions of said rotor slotsprovided within the portions of the rotor extending beyond said workingchamber, said Vane lateral extensions having projections passingradially outwardly of said working chamber and terminating medially atthe lateral ends of the slide elements, said passage communicating saidbalance chamber with the bottom of the corresponding rotor slotextending in part through said projections.

7. Engine according to claim 6 wherein each said projection contains abore passage extending from the medial end thereof adjacent thecorresponding lateral end of the slide element to the distal end thereofin communication with an end portion of the rotor slot:

8. Engine according to claim 1 wherein spring tension means arepositioned at each end of each said vane, and radially inwardly of thevane in the rotor slot, and roller means are positioned radiallyinwardly of said spring means, said spring means being seated partiallywithin a recess in the under side of said vane at the radially outwardside of said spring means and abutting a revolving goove in said rollermeans at the radially inward side of said spring means, whereby saidspring means during operation of the engine are capable of keeping saidroller means and said slide element in slight compression against theirrespective abutting parts.

9. Engine according to claim 1 wherein sliding shoe means are positionedat each end of each said vane and radially inwardly of the vane in therotor slot, and guide ring means are positioned partially medially andradially inwardly of said sliding shoe means, said shoe means beingseated partially along a recess in the under side of said vane at theradially outward side of said shoe means and seated laterally anddownwardly about said guide ring means at the radially inward side ofsaid shoe means, whereby said shoe means during operation of the engineare capable of keeping said guide ring means radially inwardly thereofand said slide element on said vane radially outwardly thereof in slightcompression against their respective abutting parts.

l0. Vane assembly, for a rotary vane type engine, which comprises alongitudinally extending vane having a top face and a bottom face, avane lateral extension being provided at each longitudinal end of thevane, each vane lateral extension having a projection passing upwardlybeyond the top face of said vane, said top face being provided with alongitudinally extending groove therein and each said projection beingprovided with a corresponding bore passage, a rocker rod extending alongsaid groove in said top face and being pivotally secured at its endswithin said bore passages, and a slide element disposed on said rockerrod and extending along said top face for pivoting with said rod.

11. Engine according to claim 10' wherein said rocker rod and slideelement are integral.

12. Engine according to claim l O wherein said rocker rod has asubstantially flat top surface and a curved bottom surface, said slideelement being secured to said rocker rod along a portion of said flattop surface, said flat top surface being received within a correspondingsubstantially fiat groove located within the bottom surface of saidslide element.

13. Engine according to claim wherein said rocker rod has asubstantially curved top surface and a bottom surface, said slideelement being secured to said rocker rod along a portion of said curvedtop surface, said curved top surface being received within acorresponding substantially curved groove located within the bottomsurface of said slide element.

-14. Engine according to claim 10 wherein said bore passage communicateswith one face of the corresponding projection of the vane extensionalong its length by means defining a slot, whereby said rocker rod maybe positioned within said bore passage through said slot.

15. Engine according to claim 14 wherein said slot is an inclined slotdefined in a side face of said projection of the vane extension passingdownwardly to said bore passage.

16. Engine according to claim 14 wherein said bore passage is ofslightly smaller diameter than that of said rocker rod and said slot isof slightly narrower width than the diameter of said bore passage,whereby said rocker rod may be positioned within said bore passage underslight tension.

17. Engine according to claim 10 wherein each projection has a top faceupwardly beyond the vane top face, and said bore passage is defined by agroove extension positioned within the bottom portion of a channeldefined in the top face of the projection of the vane extension, saidgroove extension communicating with the groove along the top face ofsaid vane, in conjunction with removable means defining a complementarytop groove positioned within said channel over said groove extension.

18. Engine according to claim 17 wherein additional means including pinmeans are provided for securing said means defining a complementary topgroove within said channel.

19. In a vane assembly, for rotary fluid machine of the type having acasing with an inner circumferential surface defining a working chamberand a rotor with slots for carrying slidable vanes in slidable sealingcontact with the casing inner surface to form intervane spaces in theworking chamber, the improvement which comprises a longitudinallyextending vane having a central portion and two end portions, said endportions extending transversely beyond said central portion, a slideelement disposed between said end portions of said vane, for cooperationwith the inner circumferential surface of the casing to form a seal, andsupport means extending into said end portions for supporting said slideelement between said two end portions.

i20. In a vane assembly, for rotary fluid machines of the type having acasing with an inner circumferential surface defining a working chamberand a rotor with slots for carrying slidable vanes in slidable sealingcontact with the casing inner surface to form intervane spaces in theworking chamber, the improvement which comprises a longitudinallyextending vane having a central portion with a top face which is smallerin height than the two end portions of the vane, said end portions eachhaving a transverse medial face adjacent said top face, sliding meanspivotal between said end portions for cooperating with the innercircumferential surface of the casing to form a sliding seal, saidsliding means having transverse end faces abutting the medial faces ofsaid end portions and cooperating therewith to form a seal therebetween,the medial faces of said end portions extending upwardly beyond theuppermost portion of the corresponding sliding means transverse endface.

21. Improvement according to claim 20 wherein means are includedextending into said end portions for pivotally supporting said slidingmeans between said end portions.

22. Improvement according to claim 21 wherein said sliding means iswider than said vane, and wherein pivotal means are included which arecarried on a retaining seat on the central portion of said vane forpivotally supporting said sliding means.

References Cited in the file of this patent UNITED STATES PATENTS1,658,524 Gurley Feb. 7, 1928 2,149,337 Deming Mar. 7, 1939 2,545,238MacMillin et a1 Mar. 13, 1951 2,658,456 Wahlmark Nov. 10, 1953 2,746,392Klessig et a1 May 22, 1956 2,755,741 Erskine July 24, 1956 FOREIGNPATENTS 9,499 Great Britain Of 1915 139,293 Austria Nov. 10, 1934568,518 Great Britain Apr. 9, 1945 606,413 Great Britain Aug. 12, 1948

1. A ROTARY VANE TYPE ENGINE COMPRISING A CASING HAVING AN INNERCIRCUMFERENTIAL SURFACE DEFINING A WORKING CHAMBER FOR RECEIVING ANDDISCHARGING FLUIDS, A ROTOR IN SAID WORKING CHAMBER HAVING AN AXISECCENTRIC WITH RESPECT THERETO AND PROVIDED WITH RADIAL SLOTS, VANESSUBSTANTIALLY RADIALLY SLIDABLE IN SAID ROTOR SLOTS AND FORMING WITHSAID ROTOR AND WITH SAID WORKING CHAMBER, EXPANDING AND CONTRACTINGINTERVANE SPACES IN WHICH SAID FLUID IS RECEIVED, SAID ROTOR EXTENDINGIN SAID CASING AXIALLY BEYOND THE AXIAL ENDS OF SAID WORKING CHAMBER ANDSAID ROTOR SLOTS IN SAID ROTOR EXTENDING AXIALLY BEYOND THE ENDS OF SAIDWORKING CHAMBER, A SLIDE ELEMENT ROCKINGLY MOUNTED LONGITUDINALLY ONEACH VANE FOR ROCKING ABOUT A LONGITUDINAL AXIS, SAID SLIDE ELEMENTHAVING A RADIALLY OUTER SIDE ADJACENT YET SPACED FROM THE CASING INNERSURFACE